US4842424A - Self-aligning track roller - Google Patents

Self-aligning track roller Download PDF

Info

Publication number
US4842424A
US4842424A US07077395 US7739587A US4842424A US 4842424 A US4842424 A US 4842424A US 07077395 US07077395 US 07077395 US 7739587 A US7739587 A US 7739587A US 4842424 A US4842424 A US 4842424A
Authority
US
Grant status
Grant
Patent type
Prior art keywords
race member
track
bearing
inner
inner race
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US07077395
Inventor
Glennwood H. Narkon
Stanley S. Orkin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kamatics Corp
Original Assignee
Kamatics Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Grant date

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02Parts of sliding-contact bearings
    • F16C33/04Brasses; Bushes; Linings
    • F16C33/28Brasses; Bushes; Linings with embedded reinforcements shaped as frames or meshed materials
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/006Guiding rollers, wheels or the like, formed by or on the outer element of a single bearing or bearing unit, e.g. two adjacent bearings, whose ratio of length to diameter is generally less than one
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02Sliding-contact bearings
    • F16C23/04Sliding-contact bearings self-adjusting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02Parts of sliding-contact bearings
    • F16C33/04Brasses; Bushes; Linings
    • F16C33/20Sliding surface consisting mainly of plastics
    • F16C33/201Composition of the plastic

Abstract

A track-roller bearing assembly is disclosed which includes a fixed inner ball race member having an outwardly facing arcuate peripheral bearing surface; an annular body of self-lubricating bearing material affixed to the outwardly bearing surface of said inner race; and a coaxial outer race which is rotatable about an axis of the inner race and angularly displaceable relative to the axis of the inner race so as to accommodate track deflections or irregularities. The track-roller further includes a resilient element disposed between respective ends of the inner and outer races so as to bias the races back into axial alignment after they have been angularly displaced relative to each other.

Description

This is a continuation-in-part of prior commonly owned application Ser. No. 567,612, filed Jan. 3, 1984, now U.S. Pat. No. 4,717,268, which was a continuation of commonly owned Ser. No. 255,634 filed Apr. 20, 1981 and now abandoned.

BACKGROUND OF THE INVENTION

The present invention relates to a track roller and more particularly, to a self-aligning track roller for accommodation to variable track surfaces comprising a co-engaging inner race and outer race movable relative to one another wherein an elastomeric element such as a ring is disposed between respective ends of the inner and outer races so as to bias the inner race into alignment with the outer race. Further, the inner race has a bearing surface provided with a self-lubricating material which is engageable with and movable relative to the bearing surface of the outer race.

At present, track rollers being used incorporate a crown radii on the outer diameter of the outer race to compensate for track deflections and irregularities. This reduces the contact area between the roller and the mating surface of the track. An increase in contact bearing pressure results due to the reduced contact area which has caused excessive wear and distress to the track surface.

Further, the conventional track roller bearings are constructed with rolling elements positioned between the inner and outer races and require a lubricant such as grease. Addition of lubricant to the rolling elements is periodically required to maintain the operational performance and to add corrosion resistance. Such bearings are subject to failure where fracturing of the rolling elements and spalling of the inner race occur. In addition, the performance of these track roller bearings depends on the effectiveness of seals incorporated therein which ensure that the grease lubrication is maintained within the varying surface area, proper, and that the grease lubrication is not contaminated from external sources.

It is known to incorporate a self-lubricating liner system as an alternative to the rolling element track roller surface of the outer race so as to operate against the bearing surface of a hardened inner race. These bearing assemblies have the advantage that they do not require periodic lubrication and they have a generally higher rolling load capacity. In addition, static radial load capacity of these bearing assemblies is substantially higher than the rolling element bearing assemblies with high thrust capacity being ensured by the use of the separate self-lubricating liner system. These self-lubricating type bearing assemblies are discussed for example in U.S. Pat. Nos. 4,048,370 and 4,134,842.

The self-lubricating liner systems with the liner attached to the inner diameter of the outer race were designed in accordance with the belief that the wear experienced during the life of the bearing system could be distributed over the full circumference of the liner and thus result in extended surface life. Nevertheless, it has been found that because of the rotation of the outer race liner in relation to the stationary inner race and the unidirectional load application, liner systems with a compression modulus of up to about 1 million psi are subjected to material deflection. More particularly, the mismatch of the inner race circumferential surface to the outer race by differential tolerances and the thickness of the liner system provide the mechanism which permits local deflection of the liner as the outer race moves relative to the inner race when loaded. Therefore, under a steady applied load, while moving in relation to the inner race, high shearing action and tensile forces are imposed on the liner immediately in front of the progressing load action of the inner race. This is known as ploughing. When combined with fluid contamination, the liner is further distressed due to the wedging action of fluid in front of the advancing inner race slider.

Lubricating material affixed to the outer race in a track-roller bearing assembly is subjected to distortion and consequent reduced service life relative to the arrangement of the present invention. The induced liner deflection when loaded by the inner race during rotation of the outer race adversely affects the bond between the lubricating material and the outer race, and as the bond fails, the lubricating material is pinched between the inner and outer races without any support and tends to be squeezed out.

SUMMARY OF THE INVENTION

The bearing assembly of the present invention overcomes the above-mentioned problems associated with the provision of a drawn radii by providing co-engaging inner- and outer races that are self-aligning. More particularly, in accordance with the present invention, an elastomeric element is provided about at least one and preferably both ends of the inner race adjacent a respective end of the outer race. In this manner, when relative angular rotation of the inner and outer races distorts the elastomeric element(s) the resiliency of the element(s) resists the deformation and urges the races into their original axial alignment.

The bearing assembly of the present invention also provides the liner bond failure occasioned by the above-described ploughing action and exhibits a significantly extended wear life. In the bearing assembly of the present invention the self-lubricating bearing material is preferably provided on the outer bearing surface of the inner material. This construction ensures positive contact between the liner system and mating surfaces so that fluid contamination does not become a mechanical wedging tool.

BRIEF DESCRIPTION OF THE DRAWING

FIG. 1 is a sectional view illustrating a first embodiment of the self-adjusting, self-lubricating track roller of the present invention;

FIG. 2 is a sectional view illustrating a second embodiment of the track roller of the present invention; and

FIG. 3 is a sectional view illustrating yet another embodiment of the present invention.

DETAILED DESCRIPTION

FIG. 1 is a sectional view of the improved bearing assembly of the present invention with the shaft omitted for clarity. As can be seen, the bearing assembly comprises an inner ball race 10 and an outer race 12 engageable with and rotatable relative to inner ball race 10. In the illustrated embodiment outer race 12 includes first and second parts 14 and 16. Further, outer race 12 has an inner arc surface defined by the inner portions of parts 14 and 16 that has a length less than the arcuate surface of inner race 10 so as to allow relative angular movement of races 10 and 12 as will be described more fully below.

Inner race 10 of the illustrated embodiment includes a ball portion 18 and first and second cylindrical portions 20. Cylindrical portions 20 extend axially beyond an associated end face 22 of outer race 12. Further, the end faces 22 are inwardly inclined so as to be conical in shape and a gap 23 is provided between the cylindrical portions 20 and the end faces 22 so that the inner and outer races 10 and 12 can be angularly displaced relative to one another to accommodate track deflections.

To provide the self-aligning characteristics of the bearing assembly, an elastomeric ring 24 is provided about at least one and preferably both cylindrical portions 20 between same and an associated end face 22. The elastomeric ring 24 so disposed is resiliently distorted when races 10 and 12 are angularly displaced because of, for example, track irregularities or other mechanical relations in a structure. However, the resiliency of ring 24 causes same to urge the races 10, 12 back into axial alignment and hence, the bearing assembly is self-aligning. As is further apparent, elastomeric ring(s) 24 also serve to cushion relative angular movement so that, despite track deflections or irregularities, motion is more smoothly transmitted while stresses on the assembly are minimized.

Referring to FIG. 2, an alternate embodiment of a self-aligning roller bearing is shown. In this embodiment, rather than wedge-shaped ring 24, realignment is provided by the combination of an O-ring 28 mounted on at least one and preferably both end portions 20 and an elastomeric washer 30 which is disposed between each O-ring 28 and its associated end face 22. Of course an appropriatly sized O-ring formed of an appropriate material could be used in some circumstances without a washer 30. Further, the illustrated embodiment, a recess 32 is defined on the surface of end portion 20 to receive O-ring 28 and retain the same in position.

Turning to FIG. 3, yet another embodiment of the present invention is shown, on an inner race that is formed with only a single end portion 34. In this embodiment, the self-aligning function is achieved through the combination of an elastomeric washer 36 disposed between an end face 38 of the outer race 40 and a rigid wedge shaped ring 43 mounted to end portion 34 of inner race 44.

The elastomeric ring(s) 24 as well as O-ring(s) 28 and washer(s) 30, 36 provided in accordance with the present invention of course may be formed from any suitable material but are preferably formed from, for example, urethane, teflon, silicone, nitrile, neoprene or vyton and may be adhesively secured in place as shown.

As can be further seen in FIGS. 1, 2 and 3, in the bearing assembly of the present invention, unlike the bearing assemblies of the prior art, the outer surface of inner race 10 is provided with a self-lubricating bearing material 26 fixedly secured thereto. Bearing material 16 can be fixed to the outer diameter of the inner race by any suitable means. The bearing material 16 so affixed is engageable with and movable relative to the inner surface of the outer race 12. Further, bearing material 16 extends the entire arc length of the inner race 10 outer diameter so that it will be disposed between outer race 12 and inner race 10 even at the extremes of relative angular motion due to track deflections or irregularities.

Outer race 12 of the bearing assembly of the present invention is made of metal, preferably stainless steel (wrought or powder metallurgy) such as 440C, 13-8PH, AMS 5617-Custom 455, 17-4PH, 300 series, and more preferably 13-8PH, although other metals such as high carbon steel 52100 as well as case hardened titantium, anodized aluminum, Inconel, Hastelloy and A286 can also be employed, so as to provide a metal inner bearing surface.

Inner race 10 of the bearing assembly of the present invention can also be made of a metal such as defined above, and more preferably stainless steel 17-4PH. The outer surface thereof has fixedly secured thereto the self-lubricating material.

The self-lubricating material can be a solid organic lubricant such as a solid polyester, polyamide, polyphenylene sulfide, polyarylsulfone, a polyfluorocarbon or, a cured acrylate as disclosed in U.S. Pat. No. 4,048,370 and incorporated herein by reference or even a woven fiber matrix impregnated, for example, with a cured acrylate composition as disclosed in U.S. Pat. No. 4,134,842 also incorporated herein by reference or other resin systems. The self-lubricating material can be secured to the outer surface 29 of inner race by known methods.

Representative polyesters include aromatic polyesters Such as p-oxybenzoyl polyester which is commercially available, for instance, under the tradename Ekanol and sold by the Carborundum Co. This polyester material has a density ranging from 1.44-1.48 gcc and a melting point of about 800° F. Polyamides usefully employed in the present invention include, for instance, Nylon-6 and Nylon-6,6 although it will be recognized that other nylon formulations can also be employed. Aromatic poly p-phenylene sulfides can also be employed and such polymers can have a molecular weight ranging as high as about 13,000. They are available, commercially, under the tradename of Ryton by Phillips Petroleum Company, such a product having a specific gravity of about 1.34, a density of about 0.0485 lbs/in3 and a melting point of about 550° F. Polyfluorocarbons usefully employed in the present invention include polytetrafluoroethylene. Included in the polyaryl sulfones suitable for use in the present invention are those which have a molecular weight ranging from about 30,000 to 60,000. One convenient polyaryl sulfone is that sold commercially under the tradename Polymer 360-3M Astrel 360 having a specific gravity of 1.36, a density of 0.049 lbs/in3, a compressive strength at 73° F. of 17,900 psi and a melting point of about 550° F. Polyimides employed in the present invention are aromatic polyimides which are available commercially under, for instance, the tradenames 6f Vespel SP-1 (DuPont) which has a specific gravity ranging from about 1.41-1.43, a density of about 0.052 lbs/in3, a compressive strength at 73° F. of about 24,000 psi and a heat distortion temperature at 264 psi of about 680° F. A modified Vespel SP-1 polyimide is Vespel SP-21 which contains 15 weight percent graphite, has a specific gravity of about 1.51, a density of about 0.0546 lbs/in3 and a compressive strength at 73° F. of about 18,000 psi. Other polyimides include one available commercially as XPl-182 by American Cyanamid which has a specific gravity of about 1.28, a density of about 0.046 lbs/in3, a compressive strength at 73° F. of about 25,000 psi and a heat distortion temperature at 264 psi of about 440° F. Still another polyimide commercially available is that sold under the tradename of Genom 3010 by General Electric and has a specific gravity of about 1.90, a density of about 0.068 lbs/in3, a compressive strength at 73° F. of about 41,900 psi and a heat distortion temperature at 264 psi of about 660° F. Polyimides containing polytetrafluoroethylene or graphite fibers can also be used.

When the self-lubricating material selected is a cured mixture of an acrylate composition and a particulate solid lubricant, such as polytetrafluoroethylene, the acrylate composition can be selected from the group consisting of

(a) a mixture of a major amount of a liquid acrylic ester selected from the group consisting of di-, tri-, and tetraesters of an acrylic acid and a polyhydric alcohol, a minor amount of a low molecular weight prepolymer of an ester of a low molecular weight alcohol having a terminal vinyl group and an aromatic polycarboxylic acid in solution in said acrylic ester and an organic amide of the formula ##STR1## wherein R is selected from the group consisting of hydrogen and aliphatic hydrocarbon of 1-20 carbon atoms in an amount sufficient to copolymerize said acrylic ester and prepolymer,

(b) a mixture of acrylic ester monomer, a peroxidic initiator in an amount sufficient to initiate polymerization of said monomer and an aminoalkoxyalkylamine of the formula R1 --N(H)R2 [OR3 ]x N(H)R4 wherein x is an integer of 1-6 inclusive, each of R1 and R4 is selected from the group consisting of hydrogen and lower alkyl and each of R2 and R3 is a lower alkyl linking bridge between N and O, in an amount sufficient to accelerate the polymerization of said monomer,

(c) a mixture of an acrylic ester of an alkyl amino alkyl alcohol and an effective amount of hydroperoxide catalyst, said acrylic ester having the formula ##STR2## wherein x is an integer of 0-5 inclusive, y is an integer of 1-6 inclusive, R is selected from the group consisting of hydrogen, halogen, hydroxy, cyano and lower alkyl and R1 is selected from the group consisting of hydrogen and alkyl having 1-6 carbon atoms,

(d) a mixture of a liquid acrylic ester monomer selected from the group consisting of diesters of an acrylic acid and a polyhydric alcohol, acrylic esters of cyclic ether alcohols, acrylic esters of amino alcohols and mixtures thereof, a peroxidic initiator and an oxyalkylamine of the formula (H)m N[(CH2)x (OR1)y OR2 ]n wherein m and n are each integers of 1 to 2 inclusive, the total of m and n is 3, x is an integer of 1 to 6 inclusive, y is an integer of 0 to 6 inclusive, R1 is lower alkyl and R2 is selected from hydrogen and lower alkyl,

(e) a mixture of an acrylic ester monomer selected from the group consisting of di-, tri- and tetraesters of an acrylic acid and a polyhydric alcohol, acrylic esters of cyclic ether alcohols, acrylic esters of amino alcohols and mixtures thereof, a peroxidic initiator of an amount sufficient to initiate polymerization of said monomer and a member selected from the group consisting of rhodanine and a hydrazide of the formula ##STR3## wherein R and R' are selected from separate groups and an interconnected group forming a cyclic ring, R is further selected from the group consisting of hydrogen, alkyl, cycloalkyl, aryl and alkoxy and R' is selected from the group consisting of hydrogen, alkyl, cycloalkyl, acyl and dithiocarbonyl in an amount sufficient to accelerate the polymerization of said monomer; and

(f) a mixture of a monomer of the formula ##STR4## wherein R1 and R are selected from the group consisting of hydrogen and lower alkyl and R is selected from the group consisting of lower alkyl, lower hydroxyalkyl, cyano and lower cyanoalkyl; at least one equivalent of an acid for each equivalent of said monomer, said acid being selected from the group consisting of acrylic acid and lower alkyl acrylic acids; an initiator selected from the group consisting of t-butyl perbenzoate, t-butyl peracetate and di-t-butyl diperphthalate, said initiator being present in an amount sufficient to initiate the polymerization of said monomer; a trihydroxy benzene inhibitor and an accelerator selected from the group consisting of benzhydrazide and N-aminorhodanine.

When the self-lubricating material selected is a woven fiber matrix impregnated with a cured acrylate composition, the woven fiber matrix can comprise a material woven from a mixture of fibers, one face of the material comprising lubricating fibers, the other comprising reinforcing fibers. Conveniently the woven fiber matrix can be fabricated from polytetrafluoroethylene fibers, as the lubricating fibers; and from such reinforcing fibers as KEVLAR fibers, polyethylene terephthalate (DACRON) fibers as well as fiberglass and graphite fibers. Preferably, the reinforcing fibers are KEVLAR fibers, available commercially under the tradename KEVLAR PRD 49, by DuPont. KEVLAR is an organic polymeric compound known as an aromatic polyamide, i.e. an aramid. It is a high strength, high modulus fiber made from long chain synthetic polyamides wherein at least 85 percent of the amide linkages are attached directly to two aromatic rings. KEVLAR fiber is extremely stable, has high strength, toughness and stiffness characteristics. The density of KEVLAR PRD 49 is 1.45 g/cc and its mechanical properties lie between the values of glass and graphite filament. The curable acrylate, which can be any of those defined above at (a) through (f) is present in an amount sufficient to impregnate the woven fiber matrix and to bond the same to the outer surface of the inner race.

As is apparent from the foregoing, to compensate for track deflections and irregularities, the track roller of the present invention is self-adjusting in that the outer race can rotate angularly relative to the axis of the inner race in response to the variable track surface. This maintains the contact area between the rolling and the mating surface of the track so that the contact bearing pressure will not be increased and excessive wear and distress of the track surface is minimized. Further, the track roller of the present invention is self-aligning in that the inner and outer races are urged back into axial alignment when the races have been so angularly displaced.

While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiment, but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.

Claims (5)

What is claimed is:
1. A track-roller bearing assembly comprising:
an inner ball race member having a central axis and an outwardly facing arcuate peripheral bearing surface, said inner race member including a cylindrical portion extending outwardly along said central axis from each end thereof;
an outer race member coaxial with said central axis of said inner race member and including a bearing portion having an annular arcuate surface, said outer race member having inwardly tapered conical end faces, said outer race member being rotatable about said central axis of said inner race member and angularly displacable relative to said axis; and
means for realigning said central axis of said outer race member with said central axis of said inner race member when said race members have rotated angularly relative to each other, said realigning means being disposed between each said cylindrical portion and a respective conical end face of said outer race member.
2. A track-roller bearing assembly as in claim 1, wherein said realigning means comprises first and second wedge-shaped annular resilient ring members, a ring member being disposed at each end of the bearing assembly.
3. A track-roller bearing assembly as in claim 2, and further comprising an annular body of self-lubricating bearing material affixed to the outwardly facing bearing surface of said inner race member; said bearing portion of said outer race member being in sliding engagement with said bearing material.
4. A track-roller bearing assembly as in claim 1, wherein said realigning means comprises at least one of an O-ring and an elastomeric washer member disposed at each end of the bearing assembly.
5. A track-roller bearing assembly as in claim 4, and further comprising an annular body of self-lubricating bearing material affixed to the outwardly facing bearing surface of said inner race member; said bearing portion of said outer race member being in sliding engagement with said bearing material.
US07077395 1981-04-20 1987-07-24 Self-aligning track roller Expired - Lifetime US4842424A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US25563481 true 1981-04-20 1981-04-20
US4717268B1 US4717268B1 (en) 1981-04-20 1984-01-03
US07077395 US4842424A (en) 1981-04-20 1987-07-24 Self-aligning track roller

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US07077395 US4842424A (en) 1981-04-20 1987-07-24 Self-aligning track roller
US07285601 US5110221A (en) 1981-04-20 1988-12-16 Self-aligning track roller

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US4717268B1 Continuation-In-Part US4717268B1 (en) 1981-04-20 1984-01-03

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US07285601 Continuation US5110221A (en) 1981-04-20 1988-12-16 Self-aligning track roller
US07285601 Continuation-In-Part US5110221A (en) 1981-04-20 1988-12-16 Self-aligning track roller

Publications (1)

Publication Number Publication Date
US4842424A true US4842424A (en) 1989-06-27

Family

ID=27373092

Family Applications (1)

Application Number Title Priority Date Filing Date
US07077395 Expired - Lifetime US4842424A (en) 1981-04-20 1987-07-24 Self-aligning track roller

Country Status (1)

Country Link
US (1) US4842424A (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5054798A (en) * 1990-03-12 1991-10-08 Arctco, Inc. Adjustable steering post with bearings
US5137374A (en) * 1981-04-20 1992-08-11 Kamatics Corporation Titanium bearing surface
US5398294A (en) * 1993-12-10 1995-03-14 Kamatics Corporation Track roller bearing
US5482379A (en) * 1993-10-01 1996-01-09 Rexnord Corporation Ball and socket bearing assembly having replaceable composite stationery ball
US6202583B1 (en) * 1998-10-08 2001-03-20 Kawasaki Jukogyo Kabushiki Kaisha Steering structure of personal watercraft
US20090275685A1 (en) * 2008-05-01 2009-11-05 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition
US20110219618A1 (en) * 2006-07-07 2011-09-15 Gerald Thomas Lien Sleeve bearing assembly and method of construction
US8021051B2 (en) 2006-07-07 2011-09-20 Federal-Mogul World Wide, Inc. Sleeve bearing assembly and method of construction
US20120141052A1 (en) * 2010-12-05 2012-06-07 New Hampshire Ball Bearings, Inc. Self lubricated bearing compositions and methods of making the same
US8735481B2 (en) 2008-05-01 2014-05-27 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition for low friction or soft substrate applications
WO2017117651A1 (en) * 2016-01-06 2017-07-13 Halliburton Energy Services, Inc. Asymmetrical radial bearing

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3108830A (en) * 1960-07-13 1963-10-29 Geneal Motors Corp Ball joint construction and method of assembly therefor
US3231299A (en) * 1960-06-15 1966-01-25 Ford Motor Co Ball joint
US4057355A (en) * 1975-07-07 1977-11-08 Ford Motor Company Frangible tie rod end bearing seat
US4447094A (en) * 1981-07-24 1984-05-08 O & S Manufacturing Company Prelubricated sealed bearings

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3231299A (en) * 1960-06-15 1966-01-25 Ford Motor Co Ball joint
US3108830A (en) * 1960-07-13 1963-10-29 Geneal Motors Corp Ball joint construction and method of assembly therefor
US4057355A (en) * 1975-07-07 1977-11-08 Ford Motor Company Frangible tie rod end bearing seat
US4447094A (en) * 1981-07-24 1984-05-08 O & S Manufacturing Company Prelubricated sealed bearings

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5137374A (en) * 1981-04-20 1992-08-11 Kamatics Corporation Titanium bearing surface
US5054798A (en) * 1990-03-12 1991-10-08 Arctco, Inc. Adjustable steering post with bearings
US5482379A (en) * 1993-10-01 1996-01-09 Rexnord Corporation Ball and socket bearing assembly having replaceable composite stationery ball
US5537746A (en) * 1993-12-10 1996-07-23 Kamatics Corporation Method of manufacture of improved track roller bearing
US5398294A (en) * 1993-12-10 1995-03-14 Kamatics Corporation Track roller bearing
US6202583B1 (en) * 1998-10-08 2001-03-20 Kawasaki Jukogyo Kabushiki Kaisha Steering structure of personal watercraft
US8021051B2 (en) 2006-07-07 2011-09-20 Federal-Mogul World Wide, Inc. Sleeve bearing assembly and method of construction
US8464427B2 (en) 2006-07-07 2013-06-18 Federal-Mogul World Wide, Inc. Sleeve bearing assembly and method of construction
US8152380B2 (en) 2006-07-07 2012-04-10 Federal-Mogul World Wide, Inc. Sleeve bearing assembly and method of construction
US20110219618A1 (en) * 2006-07-07 2011-09-15 Gerald Thomas Lien Sleeve bearing assembly and method of construction
US8034865B2 (en) 2008-05-01 2011-10-11 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition
US20110172131A1 (en) * 2008-05-01 2011-07-14 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition
US20090275685A1 (en) * 2008-05-01 2009-11-05 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition
US8735481B2 (en) 2008-05-01 2014-05-27 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition for low friction or soft substrate applications
US8741996B2 (en) 2008-05-01 2014-06-03 Roller Bearing Company Of America, Inc. Self-lubricating surface coating composition
US20120141052A1 (en) * 2010-12-05 2012-06-07 New Hampshire Ball Bearings, Inc. Self lubricated bearing compositions and methods of making the same
WO2017117651A1 (en) * 2016-01-06 2017-07-13 Halliburton Energy Services, Inc. Asymmetrical radial bearing

Similar Documents

Publication Publication Date Title
US3399008A (en) Roller cage assembly
US3542441A (en) Controlled clearance self-aligning bearing
US3977739A (en) Magnetic ball bearing assembly using ferrolubricants
US5992856A (en) Rotary, reciprocating seals with double spring and separating band rings
US5215384A (en) Self-centering squeeze film damper bearing
US4195852A (en) End face seal assembly
US4048370A (en) Shaped bearing member
US6419236B1 (en) Springclip ring
US3951418A (en) Moving captive seal construction usable under high temperature and cryogenic conditions
US5630668A (en) Thrust needle-shaped roller bearing, rolling bearing, and cage of the thrust needle-shaped roller bearing
US4767108A (en) Elastic bushing assembly
US4348031A (en) Rotary fluid seals with floating sealing rings
US4844484A (en) Floating lip seal with reinforced flexible portion
US5265965A (en) Composite ball and socket bearing with convex outer surface
US5829882A (en) Linear motion bearing assembly
US2973978A (en) Bimaterial back-up ring
US3746415A (en) Self lubricating sleeve bearing
US20030138172A1 (en) Liner motion device, rolling device and separator for rolling device
US4968044A (en) Rotary facial seal and bearing assembly
US4708499A (en) Pivot bearing for steering columns of motor vehicles
US5017022A (en) High temperature bearing
US4877272A (en) Metal static seal and assembly comprising such a seal
US3408095A (en) Swivel joints
US5984316A (en) Rotary reciprocating seals with internal metal band
US5231323A (en) Vibration isolated backup bearing for magnetic bearing

Legal Events

Date Code Title Description
AS Assignment

Owner name: KAMATICS CORPORATION, OLD WINDSOR ROAD, BLOOMFIELD

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:NARKON, GLENNWOOD H.;ORKIN, STANLEY S.;REEL/FRAME:004764/0656

Effective date: 19870921

Owner name: KAMATICS CORPORATION,CONNECTICUT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NARKON, GLENNWOOD H.;ORKIN, STANLEY S.;REEL/FRAME:004764/0656

Effective date: 19870921

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

FPAY Fee payment

Year of fee payment: 12